Device for increasing the heating and cooling output of a heat pump in heat reclamation in air conditioning units

ABSTRACT

In order to improve heat reclamation, a circulatory composite system having one heat exchanger each in a supply air volume flow and an exhaust air volume flow is provided in an air treatment system and connected to a buffer reservoir supplied by a heat pump with heat energy. In addition, a method for operating a heat reclamation system with the structure of a circulatory composite system with an integrated heat pump is designed such that the volume flow of the heat exchanger is divided in the line leading to the heat exchanger. The at least two volume flows serve to flow through the heat exchanger (compressor) of the heat pump with a larger or smaller volume flow than the heat exchanger in the supply air.

CROSS-REFERENCE TO RELATED APPLICATIONS

This patent application is the national phase of PCT/DE2008/002032,filed Dec. 4. 2008. which claims the benefit of German PatentApplication Nos. 102007059332.7, filed Dec. 7, 2007; 102007061617.3,filed Dec. 18, 2007; 102008009860.4, filed Feb. 19, 2008; and102008032201.6, filed Jul. 9, 2008.

FIELD OF THE INVENTION

The present invention relates generally to heat reclamation and moreparticularly to a device for multistage heat reclamation with controlledheating and cooling output of an air-conditioning system and to athree-stage heat reclamation system.

BACKGROUND OF THE INVENTION

Heat pumps and interconnected circulating systems are used for heatreclamation in ventilation engineering. In this case, cold external airin the form of supply air can be preheated and also dried, ifapplicable, by means of a targeted heat transfer from the warm exhaustair. Furthermore, warm external air in the form of supply air can becooled by means of heat transfer to the exhaust air. In this case, aheat transfer medium (water, brine, etc.) is frequently used fortransferring the energy.

Furthermore, interconnected circulating systems with heat pumpsintegrated therein are known. Such systems are described, for example,in DE 44 08 087 C2 and the book: Wärme- and Kälterückgewinnung inraumlufttechnischen Anlagen [Heat and Cold Reclamation in HVAC Systems],5th revised edition, 2001; ISBN 3-8041-2233-7. The efficiency of theheat reclamation can be improved with such a combination of aninterconnected circulating system and a heat pump.

Heat pumps are also used for connecting several air-conditioning deviceswith different air volume flows and air temperatures, e.g., as describedin WO 2005/072560 A1. In conventional heat reclamation systems, when theheat pump switches on, the heat transfer medium is unevenly heated andcooled because the compressor is switched on and off, leading to unevensupply air temperatures in any air-conditioning system connectedthereto. In alternative processes, controlled compressors are used orarrangements are made for controlling the cooling circuit. However, allthese measures lead to a decrease in the efficiency and to temperaturejumps in the heat transfer medium if the output of a compressor fallsbelow the minimum cooling output, because the compressor needs to beswitched off. In the cooling mode, it is also not always possible totransfer the energy introduced into the heat transfer medium by thecompressors to the exhaust air without exceeding the permissiblecondensation temperature. If the exhaust air heat exchanger ices up anda defrosting process needs to be carried out, e.g., by reversing thecooling circuit or with the aid of a bypass circuit, the cold heatexchanger cannot be replaced and the supply air heat exchanger cannot besupplied with sufficiently warm heat transfer medium in an uninterruptedfashion.

According to the device described in DE 44 08 087 C2, a partial flow ofthe heat transfer medium is decoupled from a heat exchanger such thatthe heat transfer medium can be once again fed into the flow pipe of theheat exchanger for a thermodynamic treatment. In this system, the volumeflows of the heat transfer medium are separated within the heatexchanger during operation. This results in different regions of theheat exchanger being acted upon unevenly and an inferior heat transferto be adjusted as a consequence thereof. In order to achieve an optimaldecoupling in the partial load mode, it would actually be necessary toimplement the position of the outlet point variably with respect to thelength of the heat exchanger in accordance with the respectively desiredoutput proportioning. Furthermore, the system does not feature areservoir for excess energy that is directly introduced by the heat pumpwith the condenser or evaporator in order to purposefully store energywithin the interconnected circulating system and to once again withdrawenergy therefrom in accordance with demands.

Consequently, the solutions according to the described prior art do notmake it possible to achieve a constant temperature of the heat transfermedium at the supply air heat exchanger in order to be able to set aconstant supply air temperature in interconnected circulating systems.This also applies to interconnected circulating systems with integratedheat pump, in which the heat transfer medium of the interconnectedcirculating system directly flows through the evaporator and thecondenser, particularly when they are operated in the partial load mode.An optimal heat exchange between the heat transfer medium and air overthe entire heat exchanger surface is not possible due to the differentmass flows and temperatures of the heat transfer medium. Moreover, athree-stage heat reclamation has not been disclosed so far in thedescribed context.

OBJECTS AND SUMMARY OF THE INVENTION

A device for multistage heat reclamation with controlled heating andcooling output of an air-conditioning system may contain a special unitthat features a heat pump with a hydraulic module and anenergy-buffering device, as well as a downstream heat exchanger such as,e.g., a lamellar heat exchanger. The three-stage heat reclamation systemconsists of a regenerative or recuperative heat reclamation system asthe first stage of the heat reclamation and an additional two stages ofheat reclamation. An interconnected system with integrated heat pump forseveral air-conditioning systems is provided with interconnectedcirculating systems for multistage heat reclamation and a lowtemperature-high temperature shift within the interconnected system forthe air-conditioning systems.

The invention therefore is based on the objective of providing a systemand method for preventing the aforementioned disadvantages and forsubstantially increasing the heat reclamation yield while simultaneouslyachieving adequate controllability of the supply air temperature,directly treating the heat transfer medium thermodynamically with thecondenser and the evaporator, delivering excess energy to otherconsumers, introducing energy from other heat sources and/or heat sinksinto the system, and lowering the energy input and the workload for thehydraulic devices.

These objectives are attained with an interconnected circulating systemconsisting of at least two heat exchangers connected to each other,wherein at least one heat exchanger is respectively arranged in a supplyair volume flow and in an exhaust air volume flow of an air-conditioningsystem, and wherein a buffer reservoir is connected to theinterconnected circulating system and a heat pump is integrated into theheat transfer medium circuit by means of the interconnected circulatingsystem. A system is provided for increasing the heat reclamation outputin the form of a three-stage heat reclamation system, implemented as aninterconnected circulating system described above consisting of severalrespective heat exchangers in the supply air volume flow and in theexhaust air volume flow of the air-conditioning system, wherein the heatexchangers are connected in parallel pair-by-pair or connected in seriesin the arrangement in the supply air and exhaust air volume flows.

In one aspect, the invention consists of a heat exchanger system in theform of an interconnected circulating system with integrated heat pumpand integrated buffer reservoir with a control valve. The bufferreservoir is preferably realized in the form of a stratified reservoir,wherein excess energy can be purposefully stored in and withdrawn fromthis reservoir. In addition, one or more downstream heat exchangers suchas, e.g., lamellar heat exchangers, are integrated into theinterconnected circulating system.

An increase in the return heating output is achieved if a regenerativeor recuperative heat reclamation system is provided upstream ordownstream. For example, a several respective heat exchangers in thesupply air volume flow and in the exhaust air volume flow of theair-conditioning system may be provided, wherein the heat exchangers areconnected in parallel pair-by-pair or connected in series in thearrangement in the supply air and exhaust air volume flows.

Due to the connection of several air-conditioning systems to a singleinterconnected circulating system with integrated heat pump, theinvention furthermore makes it possible to shift energy from oneair-conditioning system to another.

An economical solution for use in connection with severalair-conditioning systems featuring an interconnected circulating systemcan be realized if the interconnected system with integrated heat pumpis also used for the low temperature-high temperature shift betweenseveral air-conditioning devices. In this case, the energy withdrawnfrom one air-conditioning device (the supply air in the air-conditioningdevice is cooled) is supplied to another air-conditioning device (thesupply air in the other air-conditioning device is heated). Thecompressor only consumes power once, but the energy input has a doubleuse in this case. Air-conditioning devices that feature a regenerativeor recuperative heat reclamation system other than an interconnectedcirculating system as a first stage of the heat reclamation may also beincorporated in this case.

During the operation of the proposed system, the operating modes listedbelow may be chosen in order to reach the desired supply air temperaturewith the least effort:

1. Operation of the first stage only

2. Operation of the first stage and the interconnected circulatingsystem (without heat pump WP)

3. Operation of the first stage with the interconnected circulatingsystem and the heat pump WP

4. Supplementing the energy supply with foreign energy from an externalheating system in the heating mode, e.g., with PWT PWW

5. Supplementing the energy withdrawal from the supply air with foreignenergy from an external cold generator in the cooling mode

6. Supplementing the energy supply by means of geothermal energy in theheating mode, e.g., PWT GeoW

7. Supplementing the energy withdrawal by means of geothermal energy inthe cooling mode, e.g., PWT GeoS

8. Delivering energy to external users via PWW or PKW in the heating orcooling mode

9. Low temperature-high temperature shift from one air-conditioningdevice to another air-conditioning device

10. Low temperature-high temperature shift within an air-conditioningdevice for a reheater, e.g., in the humidity control in the coolingmode.

Due to the inventive cooperation of the device components, it ispossible to keep the supply air temperature constant or to readjust thesupply air temperature in accordance with specifications for a maximumenergy yield and a minimal input of primary energy. In the terms of VDI2071, a heat reclamation of up to 100% is achieved, wherein thetemperature level of the exhaust air may be higher or lower than thetemperature level of the supply air.

Buffer reservoirs are provided in all of the described examples. Thesebuffer reservoirs may be integrated into a heat pump unit, arranged inone of the circuits of the heat pumps in the form of a separatereservoir of various size or replaced with a partial circuit of a heatpump. However, the buffer reservoirs are each assigned, in particular,to an interconnected circulating system in order to be able to bufferthe thermal energy obtained at this location and to once again returnthe thermal energy to this location for heat transfer purposes.

Other objects and advantages of the invention will become apparent uponreading the following detailed description and upon reference to thedrawings, in which:

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 illustrates a hydraulic circuit for implementation of thedescribed principles in accordance with an embodiment of the invention;

FIG. 2 illustrates a hydraulic circuit for implementation of thedescribed principles in accordance with a further embodiment of theinvention;

FIG. 3 illustrates a hydraulic circuit for implementation of thedescribed principles in accordance with an alternative embodiment of theinvention:

FIG. 4 illustrates a hydraulic circuit for implementation of thedescribed principles in accordance with a further embodiment of theinvention:

FIG. 5 illustrates a hydraulic circuit for implementation of thedescribed principles in accordance with an alternative embodiment of theinvention;

FIG. 6 illustrates a hydraulic circuit for implementation of thedescribed principles in accordance with an alternative embodiment of theinvention;

FIG. 7 illustrates a hydraulic circuit for implementation of thedescribed principles in accordance with a further embodiment of theinvention;

FIG. 8 illustrates a hydraulic circuit for implementation of thedescribed principles in accordance with an embodiment of the invention;

FIG. 9 illustrates a hydraulic circuit for implementation of thedescribed principles in accordance with an embodiment of the invention;

FIG. 10 illustrates a hydraulic circuit for implementation of thedescribed principles in accordance with an embodiment of the invention;

FIG. 11 illustrates a hydraulic circuit for implementation of thedescribed principles in accordance with an embodiment of the invention;

FIG. 12 illustrates a hydraulic circuit for implementation of thedescribed principles in accordance with an alternative embodiment of theinvention;

FIG. 13 illustrates a hydraulic circuit for implementation of thedescribed principles in accordance with a further embodiment of theinvention;

FIG. 14 illustrates a hydraulic circuit for implementation of thedescribed principles in accordance with an embodiment of the invention;

FIG. 15 illustrates a hydraulic circuit for implementation of thedescribed principles in accordance with an alternative embodiment of theinvention;

FIG. 16 illustrates a hydraulic circuit for implementation of thedescribed principles in accordance with a further embodiment of theinvention;

FIG. 17 illustrates a hydraulic circuit for implementation of thedescribed principles in accordance with a further embodiment of theinvention; and

FIG. 18 illustrates a hydraulic circuit for implementation of thedescribed principles in accordance with an alternative embodiment of theinvention.

While the invention is susceptible of various modifications andalternative constructions, a certain illustrative embodiment thereof hasbeen shown in the drawings and will be described below in detail. Itshould be understood, however, that there is no intention to limit theinvention to the specific form disclosed, but on the contrary, theintention is to cover all modifications, alternative constructions, andequivalents falling within the spirit and scope of the invention.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

In a preferred embodiment, a circuit according to FIG. 1 is used. Thehydraulic circuit is connected in such a way that it forms aninterconnected circulating system when the compressor of the heat pumpWP is switched off. FIG. 1 shows the basic incorporation of a bufferreservoir into an interconnected circulating system. In this case, thebuffer reservoir may be realized in the form of a so-called stratifiedreservoir, wherein thermal energy can be stored in and withdrawn fromthis reservoir layer-by-layer. This is realized due to the correspondingconnection with the supply lines PU, PO and the three-way valve V6. Theheat pump WP furthermore is assigned to the buffer reservoir in order tosupply thermal energy to this buffer reservoir.

Regarding Operating Mode 1:

Referring to the system of the FIG. 1, Operating mode 1 occurs when thecompressor is switched off and without using the heat pump WP.

The heat transfer medium is conveyed in the hydraulic circuit by a pump(e.g., a feed pump of the heat pump WP) and flows through the pipelinesand valves of the system in the following sequence: the line L6-A, thevalve V5, the line L9, the valve V6, the line L10, the heat exchangerLWT2, the line L4, the valve V1, the lines L1-E, L1-A, the heatexchanger LWT1, the lines L3-A, L3-Z and back into the heat pump WP viathe line L6-E.

In this case, the heat transfer medium flows through the condenser andthe evaporator of the heat pump WP and no energy is withdrawn orsupplied within the heat pump WP that is switched off. The feed pumpcontained in the heat pump WP is used as a circulating pump for thehydraulic circuit.

Regarding Operating Mode 2:

Referring to the system of the FIG. 1, Operating mode 2 occurs when thecompressor is switched off and the buffer reservoir P1-1 is empty:

When the heat pump WP is switched on, the heat transfer medium flowingthrough the evaporator flows through the pipelines and valves as followsin the heating mode: the line L1-A, the heat exchanger LWT1, the linesL3-A, L7, the valve V1 and back into the heat pump WP via the line L1-E.The heat transfer medium flowing through the condenser of the heat pumpWP subsequently flows through the line L6-A, the valve V5, the line L9,the valve V6, the line L10, the heat exchanger LWT2, the lines L4, L8,the valve V4, the line L3-Z and back into the heat pump WP via the lineL6-E. Excess energy introduced by the heat pump WP is transported intothe buffer reservoir P1-1 with the heat transfer medium via the valve V5and the line L11 and displaces the cold heat transfer medium stored inthe buffer reservoir P1-1, wherein this cold heat transfer medium exitsthe buffer reservoir P1-1 through the line PU and flows through the lineL9 and to the valve V6. The required heat transfer medium temperaturefor achieving the desired supply air temperature is adjusted with thevalve 6.

Regarding Operating Mode 3:

Referring to the system of the FIG. 1, Operating mode 3 occurs when thecompressor is switched off and the buffer reservoir P1-1 is full:

The compressors of the heat pump WP are switched off when the bufferreservoir P1-1 is filled with warm heat transfer medium. The hydrauliccircuit is connected as described under operating mode 1. The amount ofwarm heat transfer medium required for reaching the desired temperaturein the line L10 is withdrawn from the buffer reservoir P1-1 via the linePO by means of the valve V6. The same quantity of cold heat transfermedium as that withdrawn through the line PO is supplied to the bufferreservoir P1-1 through the line PU 1. In this case, energy is alsowithdrawn from the exhaust air by means of the heat exchanger LWT1 whenthe compressors are switched off.

An improvement in the heat reclamation is achieved if the system isrealized in the form of a two-stage heat reclamation with a first stagein the form of a regenerative or recuperative heat reclamation system.The corresponding device is illustrated in FIG. 2.

Regarding Operating Mode 4:

Referring to the system of the FIG. 2, Operating mode 4 occurs when thecompressor is switched on:

In the system shown in this figure, an interconnected circulating systemthat is referred to as stage 1 is provided between the supply airchannel and the exhaust air channel as the first stage of the heatreclamation. Stage 1 of the heat reclamation withdraws energy from theexhaust air and transfers this energy to the supply air. The secondstage of the heat reclamation is connected as follows: the heat transfermedium flows from the evaporator of the heat pump WP through the lineL1-A, the valve V8, S2, the lines L3-A and L7, the valve V1 and the lineL3-A. The heat transfer medium flows from the condenser of the heat pumpWP through the line L6-A, the valve V5, the line L9, the valve V6, theline L10, the heat exchanger LWT2, the line L4, the line L8, the valveV4, the line L3-Z and subsequently the line L6-E. During this process,excess energy can be once again stored in the buffer reservoir P1-2. Theheat transfer medium does not flow through the heat exchanger LWT3 inthis case.

Operating Mode 5:

Referring to the system of the FIG. 2, Operating mode 5 occurs when thecompressor of the heat pump WP is switched off:

An interconnected circulating system is formed when thecompressor/compressors of the heat pump WP is/are switched off. The heattransfer medium flows through the valve V1, the valve V7, the heatexchanger LWT3, the line L3A, the line L3-Z, the line L6-E, the lineL6-A, the valves V5 and V6, the line L10, the heat exchanger LWT2, theline L4 and once again through the valve V1. If required, energy fromthe filled buffer reservoir P1-2 can be admixed again.

If ice forms in the heat exchanger LWT1, the valve V8 is closed and thevalve V9 is opened. Subsequently, the circulating pump P1 conveys theheat transfer medium through the heat exchanger LWT1 that is heated totemperatures above 0° C. with the electric heater battery Erh in a smallcircuit.

The invention essentially pertains to a method for operating a heatreclamation system with the structure of an interconnected circulatingsystem with integrated heat pump, in which the volume flow of the heattransfer medium is divided into at least two volume flows in the lineleading to the heat exchanger. Due to these measures, a larger orsmaller volume flow than that flowing through the heat exchanger in thesupply air volume flow can flow through the heat exchanger (evaporator)of the heat pump WP. This makes it possible to adjust the largesttemperature difference possible in the heat exchangers of theinterconnected circulating system and the smallest temperaturedifference possible in the heat exchangers of the heat pump. The firsteffect results in an exceptionally efficient heat transfer in theinterconnected circulating system. The latter effect has very positiveeffects on the operating mode of the heat pump and its compressors.

The core of the invention is, in particular, a method for operating aninterconnected circulating system with integrated heat pump, in which apartial flow of the heat transfer medium is decoupled between theexhaust air heat exchanger and the supply air heat exchanger. Thedecoupled partial flow is subsequently treated thermodynamically byadding thermal energy to or withdrawing thermal energy from this partialflow. Prior to entering the supply air heat exchanger, the decoupled andnow altered partial flow of the heat transfer medium is once againcombined with the previously remaining other partial flow. Due to themixing of the two partial flows with different temperatures, the heattransfer medium temperature can be precisely mixed to the heat transfermedium temperature required for reaching the supply air temperatureprior to entering the supply air heat exchanger. The partial flowdecoupled for the thermodynamic treatment is conveyed through thecondenser by means of a circulating pump integrated into the heat pumpin the heating mode and through the evaporator in the cooling mode. Dueto these measures, a larger or smaller volume flow than that flowingthrough the (lamellar) heat exchanger in the supply air can flow throughthe heat exchanger (e.g., evaporator or condenser) of the heat pump.Consequently, the largest possible temperature difference can beadjusted in the heat exchangers of the interconnected circulating systemand the smallest possible temperature difference can be adjusted in theheat exchangers of the heat pump. This results in a very effective heattransfer in the interconnected circulating system and a significantlyimproved operating mode of the heat pump and its compressors. It isimportant that a reservoir is provided in the system for bufferingexcess energy that might be introduced into the system by thecompressor.

An additional increase of the heat reclamation is achieved with acircuit according to FIG. 9.

In this case, the division of the different volume flows of the heattransfer medium for the operation of the heat pump and the lamellar heatexchanger is preferably realized with an admixing circuit or with aninjecting circuit for the incorporation of the condenser and theevaporator. In order to increase the return heating output, several heatexchangers may be connected in series in the supply air volume flow, aswell as in the exhaust air volume flow. An additional increase of thereturn cooling output of the heat pump WP during the cooling of thesupply air is achieved if an adiabatic humidifier is placed between theheat exchangers LWT2-1 and LWT2-3. Due to the incorporation of devicessupplying geothermal energy into the line L2V-E, the geothermal heat canalso be introduced into the system in the heating mode such that theperformance of the heat pump WP is further improved.

In case ice forms on the heat exchangers LWT2-1 or LWT2-3, the returnheating output of the heat exchangers can be reduced for defrostingpurposes. During the defrosting process, the heat pump WP withdraws therequired energy from the device that supplies geothermal energy.

Regarding Operating Mode 6:

Referring to the system of the FIG. 3, Operating mode 6 occurs when thecompressor of the heat pump WP is switched on:

A circulating pump (feed pump of the heat pump WP) conveys the heattransfer medium through the evaporator of the switched-on heat pump WPthat cools down during this process. The heat transfer mediumsubsequently flows through the line L2V-A. A partial flow is returned tothe evaporator of the heat pump WP via the line L2-4, the valve V2-3 andthe line L2V-E and the remaining volume flow enters the line L2-3, flowsthrough the heat exchanger LWT2-1 and into the line L2-1. A partial flowis withdrawn from the line L2-1 via the line L2K-E, flows to thecondenser of the heat pump WP via the valve V2-2, through an optionalbuffer reservoir P2-1 and the line L2K-A and then back into the lineL2-1. A partial flow is previously returned to the condenser via theline L2-2, the valve V2-2 and the line L2K-E in order to increase thevolume flow. The heat transfer medium flows from the line L2-1 into theheat exchanger LWT2-2, the line L2-3, the valve V2-1 and then into theheat exchanger LWT2-1. A partial flow is previously withdrawn andreturned to the evaporator via the line L2V-E and the valve V2-3.

Regarding Operating Mode 7:

Referring to the system of the FIG. 3, Operating mode 7 occurs when thecompressor of the heat pump WP is switched off:

The heat transfer medium flows through the heat exchanger LWT2-1, theline L2-1, the valve V2-2, the line L2K-E, the buffer reservoir P2-1,the line L2K-A, the line L2-1, the heat exchanger LWT2-2, the line L2-3and then the valve V2-1. At high energy content in the buffer reservoirP2-1, a partial flow of the heat transfer medium can be returned to thecondenser of the heat pump WP during this process via the line L2-2 andthe valve V2-2.

In FIG. 4, the reservoir is moved out of the heat pump WP and realizedin the form of a stratified reservoir.

Regarding Operating Mode 8:

Referring to the system of the FIG. 4, Operating mode 8 occurs when thecompressor of the heat pump WP is switched on:

A circulating pump (feed pump of the heat pump WP) conveys the heattransfer medium through the evaporator of the switched-on heat pump WPthat cools down during this process. Subsequently, the heat transfermedium flows through a line L2V-A. A partial flow is returned to theevaporator via a line L2-4, the valve V2-3 and the line L2V-E and theremaining volume flow enters the line L2-3 and flows through the heatexchanger LWT2-1 and into the line L2-1. A partial flow is withdrawnfrom the line L2-1 via the line L2K-E and flows to the condenser of theWP via the valve V2-2. The heat transfer medium flows back into the lineL2-1 via the line L2K-A, the valve V2-5, the line L2-7, the valve V2-6and the line L2-9. A partial flow for increasing the volume flow ispreviously returned to the condenser via line L2-2, valve V2-2, and lineL2K-E. If excessive energy is introduced, a portion of the heat transfermedium is stored in the reservoir. The heat transfer medium flows fromthe line L2-1 into the heat exchanger LWT2-2, then through the line L2-3and the valve V2-1 and is subsequently divided. A partial flow is suckedinto the line L2V-E for this purpose.

Regarding Operating Mode 9:

Referring to the system of the FIG. 4, Operating mode 9 occurs when thecompressor of the heat pump WP is switched off:

The circulating pump (feed pump of the heat pump WP) conveys the heattransfer medium through the evaporator of the heat pump WP. The heattransfer medium subsequently flows through the line L2V-A, enters theline L2-3 and flows through the heat exchanger LWT2-1 and into the lineL2-1. A partial flow is withdrawn from the line L2-1 via the line L2K-Eand flows to the condenser of the heat pump WP via the valve V2-2. Theheat transfer medium flows back into the line L2-1 via the line L2K-A,the valve V2-5, the line L2-7, the valve V2-6 and the line L2-9. If theheat transfer medium is not sufficiently warm for reaching the desiredsupply air temperature, warm heat transfer medium from the bufferreservoir P2-1 is admixed. The heat transfer medium flows from the lineL2-1 into the heat exchanger LWT2-2, then through the line L2-3 and thevalve V2-1 and reenters the heat exchanger LWT2-1.

Regarding Operating Mode 10:

Referring to the system of the FIG. 5:

Corresponds to FIG. 4 with simpler energy buffering in a bufferreservoir outside the heat pump module.

Regarding Operating Mode 11:

Referring to the system of the FIG. 6, Operating mode 11 occurs when thecompressor switched on while cooling the supply air volume flow:

The supply air is cooled to the desired temperature with the previouslycooled heat transfer medium in the heat exchanger LWT2-2 such that theheat transfer medium is heated up. Subsequently, the heat transfermedium flows into the line L2-3, from which a partial flow is withdrawnvia the line L2-5 and flows into the line L2-1 via the valve V2-4. Afterthe withdrawal from the line L2-3, the heat transfer medium flows intothe line L2V-E via the valve V2-1, wherein the heat transfer mediumflows from the valve V2-3 to the condenser of the heat pump WP and ispumped into the line L2V-4 leading to the heat exchanger LWT2-1 by theintegrated circulating pump of the hydraulic module of the heat pump WP.A partial flow is once again withdrawn via the line L2-4 and flows tothe condenser that again raises the temperature level via the valveV2-3. The heat transfer medium cools down in the heat exchanger LWT2-1.The heat exchanger LWT2-1 is realized in the form of a hybrid coolersuch that a high return cooling output of the heat exchanger LWT2-1 isachieved. The required cooling of the air and the oversaturation withwater is realized with the humidifier 2-1. The heat transfer mediumreaches the heat exchanger LWT2-3 via S2-2 and additionally cools downtherein.

The heat transfer medium continues to flow to the geothermal stationGeoS via the line L2.1, in which energy can be optionally withdrawn bymeans of a device for incorporating geothermal energy. Subsequently, thevolume flow of the heat transfer medium is once again divided, whereinone partial flow continues to flow in the direction of the heatexchanger LWT2-2 and the other partial flow flows to the evaporator ofthe heat pump WP via the line L2K-E and the valve V2-2. The circulatingpump integrated into the hydraulic module of the heat pump WPadditionally conveys the heat transfer medium into the line L2-1 via theline L2K-A and the heat exchanger ENW-A. A partial flow once again ispreviously withdrawn from the line L2K-A via the line L2-2 and the valveV2-2 and returned to the evaporator in order to be additionally cooled.During the humidity control of the supply air volume flow, the air thatwas previously cooled by means of the heat exchanger LWT2-2 is broughtto the desired supply air temperature.

Regarding Operating Mode 12:

Referring to the system of the FIG. 6, Operating mode 12 occurs when thecompressor is switched off while cooling the supply air volume flow:

The heat transfer medium flows through the heat exchanger LWT2-2 suchthat the supply air is cooled down, wherein the heat transfer mediumsubsequently flows through the line L2-3, the valve V2-1, the lineL2V-E, the heat exchanger LWT2-1, S2-2, the heat exchanger LWT2-3 andthe line L2-1 and then reenters the heat exchanger LWT2-2. A partialflow is previously withdrawn via the line L2K-E and conveyed to theevaporator via the valve V2-2. The cold energy transfer medium from thebuffer reservoir is admixed to the heat transfer medium in the hydraulicmodule until the heat transfer medium has the temperature required forreaching the supply air temperature.

Regarding Operating Mode 13:

Referring to the system of the FIG. 6, Operating mode 13 occurs when thecompressor switched on while heating the supply air volume flow:

The supply air is heated to the desired temperature with previouslyheated heat transfer medium in the heat exchanger LWT2-2, wherein theheat transfer medium subsequently cools down, exits the heat exchangerLWT2-2 via the line L2-3 and flows into the heat exchanger ENK-E, inwhich energy obtained, e.g., from geothermal sources or waste water canbe supplied to the heat transfer medium, via the valve V2-1, the lineL2V-E and the valve V2-3. Subsequently, the circulating pump conveys theheat transfer medium through the evaporator such that it exits the heatpump WP via the line L2V-A and flows into the heat exchanger ENK-A, inwhich energy can be decoupled, for example, in order to cool a serverspace. A partial flow once again flows into the evaporator circuit viathe line L2-4 and the valve V2-3 while the other partial flow flows inthe direction of the heat exchanger LWT2-1, is supplied with energytherein and then flows to the heat exchanger LWT2-3, in which the heattransfer medium is additionally heated, via the line S2-2. From the heatexchanger LWT2-3, the heat transfer medium flows into the line L2-1leading to the heat exchanger LWT2-2. A partial flow is withdrawn fromthe line L2-1 via the line L2K-E and pumped to the condenser of the heatpump WP, in which the heat transfer medium is heated, via the valveV2-2. The heat transfer medium subsequently flows to the heat exchangerENW-A via the line L2K-A. The heat exchanger ENW-A makes it possible todecouple energy, e.g., in order to supply a floor heater or concretecore activation. The volume flow once again divides at the connection ofthe line L2-2 to the line L2K-A and one partial flow flows to the heatexchanger LWT2-2 while the other partial flow is returned to thecondenser via the line L2-2, the valve V2-2 and the line L2K-E.

During an adiabatic humidification of the supply air volume flow, theair cooled by the humidifier 2-3 is brought to the desired supply airtemperature.

Regarding Operating Mode 14:

Referring to the system of the FIG. 6, Operating mode 14 occurs when thecompressor switched off while heating the supply air volume flow:

The heat transfer medium flows through the heat exchanger LWT2-2 suchthat the supply air is heated, wherein the heat transfer mediumsubsequently flows through the line L2-3, the valve V2-1, the lineL2V-E, the heat exchanger LWT2-1, S2-2, the heat exchanger LWT2-3, theline L2-1 and the geothermal station GeoS and then reenters the heatexchanger LWT2-2. A partial flow is previously withdrawn via the lineL2K-E and conveyed to the condenser via the valve V2-2. Warm heattransfer medium from the buffer reservoir is admixed to the heattransfer medium in the hydraulic module until the heat transfer mediumhas the temperature required for reaching the supply air temperature.

Regarding Operating Mode 15:

Illustrated in FIG. 7:

The heat transfer medium flows through the heat exchanger LWT2-2,subsequently through the line L2-3, the valve V2-1, the heat exchangerLWT2-1 and the line L2-1 and then back into the heat exchanger LWT2-2. Apartial flow is withdrawn from the line L2-1 via the line L2K-E,conveyed via the valve V2-2 to the condenser in the heating mode or tothe evaporator in the cooling mode through the buffer reservoir of thehydraulic module by means of the first circulating pump contained in thehydraulic module of the heat pump WP and then flows into the line L2-1via the line L2K-A.

A partial flow is again previously withdrawn via the line L2-2 andconveyed to the condenser or evaporator via the valve V2-2 and the lineL2K-E. In order to transfer the energy of the heat pump WP to theexhaust air volume flow, the second circulating pump contained in thehydraulic module of the heat pump WP conveys the heat transfer mediumthrough the line L2M-A, the heat exchanger LWT2-5 and the line L2M-A.

Regarding Operating Mode 16:

Illustrated in FIG. 8:

In this illustration, the device corresponds to above-describedoperating mode 15. However, a supplementary main circulating pump P2 isprovided and subsequently conveys the heat transfer medium in such a waythat a constant or controlled flow through the lamellar heat exchangersLWT2-1 and LWT2-2 is ensured.

Regarding Operating Mode 17:

Illustrated in FIG. 9:

In this case, the device is realized in accordance with the devicesdescribed above with reference to operating mode 6. A supplementary maincirculating pump P2 is also provided in this case in order to achieve aconstant or controlled flow through the lamellar heat exchangers LWT2-1and LWT2-2.

Another embodiment is illustrated in FIGS. 10 and 11.

Regarding Operating Mode 18:

Illustrated in FIG. 10:

The heat transfer medium flows from the heat exchanger LWT2-2 into theline L2-3 and back into the heat exchanger LWT2-2 via the valve V2-1,the heat exchanger LWT2-1 and the line L2-1. A partial flow of the heattransfer medium is then withdrawn from the line L2-1 via the line L2K-E,wherein the partial flow is conveyed via the valve V2-2 to the combinedcondenser/evaporator through the buffer reservoir of the hydraulicmodule by means of the circulating pump contained in the hydraulicmodule of a heat pump WP and subsequently flows into the line L2-1 viathe line L2K-A. A partial flow of the heat transfer medium once again ispreviously withdrawn via the line L2-2 and conveyed to the combinedcondenser/evaporator via the valve V2-2 and the line L2K-E. The transferof the energy of the heat pump WP to the heat exchanger LWT2-5 in theexhaust air volume flow is realized with the coolant lines L2M-A andL2M-A.

Regarding Operating Mode 19:

Illustrated in FIG. 11:

In this case, a constant or controlled flow through the lamellar heatexchangers LWT2-1 and LWT2-2 is realized in accordance with operatingmode 18, however, with a main circulating pump P2.

Another embodiment is illustrated in FIGS. 12, 13 and 14.

Regarding Operating Mode 20:

Illustrated in FIG. 12 for heat reclamation:

A heat exchanger for introducing additional energy from a heat pump isintegrated into an interconnected circulating system that is referred toas 1st stage 4-1. The heat pump withdraws additional energy from theexhaust air flow downstream of the interconnected circulating system bymeans of lamellar heat exchangers LWT4-1 or/and LWT4-2 and delivers thisenergy to the supply air by means of the heat exchanger integrated intothe interconnected circulating system, in which the heat transfer mediumfrom the interconnected circulating system with the heat exchanger isadditionally heated. The respectively required heat transfer medium isconveyed to the heat exchanger with the aid of the valve group V4-G,wherein the feed pipe and the return pipe for the warm or the cold heattransfer medium are each opened during this process.

Regarding Operating Mode 21:

Illustrated in FIG. 12 for low temperature-high temperature shift:

The three-way valve in the interconnected circulating system 1st stage4-1 is adjusted such that no heat transfer medium can flow through theexhaust air heat exchanger. Energy is withdrawn from the heat transfermedium with the heat pump by means of the heat exchanger incorporatedinto the interconnected circulating system such that the supply air ofan HVAC device RLG1 is cooled. The withdrawn energy is delivered to theinterconnected circulating system 1st stage 4-2 for the supply air of anHVAC device RLG2 via the hydraulic circuit of the heat pump byadditionally heating the heat transfer medium by means of theinterconnected circulating system 1st stage 4-2 with the integrated heatexchanger.

Regarding Operating Mode 22:

Illustrated in FIG. 13:

FIG. 13 shows a somewhat less complicated pipe arrangement that makes itpossible to simultaneously utilize both HVAC devices RLG1, RLG2 forheating or for cooling purposes.

Regarding Operating Mode 23:

Illustrated in FIG. 14:

FIG. 14 shows the utilization of an interconnected circulating system asthe first stage of the HVAC device RLG1 and a rotating air-to-air heatexchanger as the first stage of the HVAC device RLG2. The connection ofthe HVAC devices RLG1 and RLG2 is produced by the heat pump WP withintegrated hydraulic module as described above with reference tooperating mode 20 and operating mode 22.

Regarding Operating Mode 33:

FIG. 15 essentially shows the illustration according to FIG. 12 or 13 inwhich a KVS is used as the first stage of the HVAC device RLG1 and aKVSs is used as the first stage of the HVAC device RLG2. The connectionof the HVAC devices RLG1 and RLG2 is produced by the heat pump WP withintegrated hydraulic module as described above with reference tooperating mode 20 and operating mode 22. In this case, no heat exchangeris provided for the heat transfer into the circuit of the heat pump WPsuch that the same heat transfer medium as in the interconnectedcirculating systems is used in this case.

A recooling device eK is illustrated outside of each of theair-conditioning units in numerous figures. In the cooling mode, therecooling device eK makes it possible to transfer a quantity of energyto the outside air that could not be transferred or that could betransferred only inefficiently with the heat exchangers in the exhaustair volume flow. In this case, it is particularly advantageous if theheat transfer medium initially flows through the recooler outside theair-conditioning units because the outside air used for cooling purposesis generally warmer than the exhaust air temperature. The heat transfermedium can then be cooled down to a lower temperature level with theexhaust air temperature.

LIST OF REFERENCE SYMBOLS

AU Outside air volume flow

AB Exhaust air volume flow

2-1 A diabatic Adiabatic humidifier

2-2 A diabatic humidifier

2-3 A diabatic humidifier

LWT1 Lamellar heat exchanger, exhaust air

LWT2 Lamellar heat exchanger, supply air

LWT3 Lamellar heat exchanger, exhaust air

LWT2-1 Lamellar heat exchanger, exhaust air

LWT2-2 Lamellar heat exchanger, supply air

LWT2-3 Lamellar heat exchanger, exhaust air

LWT2-4 Lamellar heat exchanger, supply air

LWT2-5 Lamellar heat exchanger, exhaust air

LWT2-6 Lamellar heat exchanger, exhaust air realized in the form of acombined condenser/evaporator

L3 A Pipeline

L3 Z Pipeline

L6 E Pipeline

L6 A Pipeline

L7 Pipeline

L8 Pipeline

L9 Pipeline

L10 Pipeline

L11 Pipeline

L2F A Coolant pipeline

L2F E Coolant pipeline

L2K A Pipeline

L2K E Pipeline

L2M A Pipeline

L2M E Pipeline

L2N A Pipeline

L2N E Pipeline

L2V A Pipeline

L2V E Pipeline

L2-1 Pipeline

L2-2 Pipeline

L2-3 Pipeline

L2-4 Pipeline

L2-5 Pipeline

L2-6 Pipeline

L2-7 Pipeline

L2-8 Pipeline

L2-9 Pipeline

S2-2 Pipeline

ENK-A Heat exchanger for decoupling energy for external consumers at lowtemperature level

ENK-E Heat exchanger for introducing external energy, e.g., geothermalenergy or

energy obtained from wastewater

ENW-A A Heat exchanger for decoupling energy for external consumers athigh temperature level

PO Pipeline

PU Pipeline

PWW Heat exchanger for introducing external energy, e.g., with pumpedhot water

PKW Heat exchanger for introducing external energy, e.g., with pumpedcold water

V1 Valve

V2-1 Valve

V2-2 Valve

V2-3 Valve

V2-4 Valve

V2-5 Valve

V2-6 Valve

V4 Valve

V4 Valve

V4-G Valve group

V5 Valve

V6 Valve

V7 Valve

V8 Valve

V9 Valve

VSR Balancing valve or volume flow controller

WP Heat pump with integrated hydraulic module including circulatingpumps

and buffer reservoirs and change-over valves for reversible operation

K Optional recooler for transferring excess energy to outside air

P1 Circulating pump

Buffer reservoir External reservoir for buffering energy; stratifiedreservoir

P2-1 External reservoir for buffering energy realized in the form of astratified reservoir

P2-2 External reservoir

Stage 1 Regenerative or recuperative heat reclamation system

RLG1HVAC device 1

RLG2HVAC device 2

1-34. (canceled)
 35. An interconnected circulating system consisting ofat least two heat exchangers connected to each other, wherein at leastone heat exchanger is respectively arranged in a supply air volume flowand in an exhaust air volume flow of an air-conditioning system, andwherein a buffer reservoir is connected to the interconnectedcirculating system and a heat pump is integrated into the heat transfermedium circuit by means of the interconnected circulating system. 36.The interconnected circulating system according to claim 35 consistingof several respective heat exchangers in the supply air volume flow andin the exhaust air volume flow of the air-conditioning system, whereinthe heat exchangers are connected in parallel pair-by-pair or connectedin series in the arrangement in the supply air and exhaust air volumeflows.
 37. The interconnected circulating system according to claim 35with one or more respective heat exchangers in the supply air andexhaust air volume flows, wherein a buffer reservoir is integrated intothe heat transfer medium circuit by means of the heat exchanger orconnected to the interconnected circulating system.
 38. Theinterconnected circulating system according to claim 37, wherein thebuffer reservoir is arranged in the flow of the heat transfer mediumdownstream of the device for thermodynamically treating the heattransfer medium and upstream of a heat exchanger in the supply airvolume flow and/or exhaust air volume flow.
 39. The interconnectedcirculating system according to claim 35, in which the buffer reservoiris integrated into the heat transfer medium circuit of the condenser orthe buffer reservoir is integrated into the heat transfer medium circuitof the evaporator.
 40. The interconnected circulating system accordingto claim 35, in which the buffer reservoir is integrated into the heattransfer medium circuit of a combined condenser/evaporator of a heatpump that can be changed over in the cooling circuit.
 41. Theinterconnected circulating system according to claim 35, in which thebuffer reservoir is integrated into the heat transfer medium circuit ofan active evaporator or active condenser of a heat pump that can bechanged over on the hydraulic side, wherein the active evaporator or theactive condenser is used for the supply air.
 42. The interconnectedcirculating system according to claim 35 with integrated heat pump,wherein a partial flow of the heat transfer medium is decoupled betweenthe exhaust air and supply air heat exchangers, wherein the decoupledpartial flow of the heat transfer medium is conveyed to a thermodynamictreatment device and recombined with the remaining partial flow of theheat transfer medium before entering the supply air heat exchanger. 43.A method for operating a heat reclamation system with the structure of ainterconnected circulating system that respectively features one or moreheat exchangers in a supply air volume flow and an exhaust air volumeflow, as well as an integrated heat pump, characterized in that thevolume flow of the heat transfer medium is divided into at least twovolume flows in the line leading to the heat exchanger such that alarger or smaller volume flow than that flowing through the heatexchanger in the supply air volume flow can flow through the heatexchanger (such as the evaporator or condenser) of the heat pump. 44.The method according to claim 43, wherein the method is controlled insuch a way that a larger or smaller volume than that flowing through theheat exchanger in the exhaust air can flow through the heat exchanger(condenser) of the heat pump.
 45. The method according to claim 43,wherein the method is controlled in such a way that a larger or smallervolume flow than that flowing through the heat exchanger in the supplyair can flow through the heat exchanger (combined condenser/evaporator)of the heat pump that can be changed over on the cooling side.
 46. Themethod according to claim 43, wherein the method is controlled in such away that a larger or smaller volume flow than that flowing through theheat exchanger in the supply air can flow through the heat exchanger,condenser or evaporator of the heat pump that is active in the supplyair volume flow and can be changed over on the hydraulic side.
 47. Themethod according to claim 43, in which external energy is introducedinto the partial circuit of the evaporator.
 48. The method according toclaim 43, in which energy for an external consumer is decoupled into thepartial circuit of the evaporator or energy for an external consumer isdecoupled into the partial circuit of the condenser.
 49. The methodaccording to claim 43, in which a humidifier is incorporated into theexhaust air volume flow between two series-connected heat exchangers forthe adiabatic humidification.
 50. A device for three-stage heatreclamation consisting of an interconnected circulating system with atleast one respective heat exchanger arranged in an exhaust air volumeflow and in a supply air volume flow, with an integrated heat pump andwith an upstream or downstream regenerative or recuperative heatexchanger.
 51. The Device according to claim 50 with multiple heatexchangers that are connected in series in the supply air volume flowand/or with several heat exchangers that are connected in series in theexhaust air volume flow.
 52. The Device according to claim 50 with adefrosting device featuring an electric heater for the heat exchanger inthe exhaust air.
 53. The Device according to claim 50 with a heatexchanger and external energy from a heating system.
 54. The Deviceaccording to claim 50 with additional electric heating rods in the heatexchanger in the exhaust air.
 55. The Device according to claim 50 forconnecting multiple HVAC devices for multistage heat reclamation,wherein the first stage of the heat reclamation of the air-conditioningdevices consists of an interconnected circulating system.
 56. The Deviceaccording to claim 50 for connecting multiple HVAC devices formultistage heat reclamation, wherein the first stage of the heatreclamation of the air-conditioning devices selectively consists of aninterconnected circulating system or another regenerative orrecuperative heat reclamation system.